Vibratory straightening machines



July 4, 1967 J. H. ROHU-S 3,328,995

VI BRATORY STRA IGHTEN I NG MACHINES Filed Deo. 2l, 1964 3 Sheets-Sheetl F/G. g2

5f y y 64 62 A ATTORNEYS July 4, 1967 .1, H RoHLFs VIBRATORYSTRAIGHTENING MACHINES 3 Sheets-Sheet-2 Filed Deo. 2l, 1964 July `4,1967 J, H, RQHLFS' A 3,328,995

VIBRATORY STRAIGHTENING MACHINES Filed Dec. 2l, 1964 This inventionrelates to a vibratory straightening machine for straightening elongatedworkpieces.

4It is the general object of the present invention to provide astraightening machine which is particularly adapted to accommodaterelatively small elongated workpieces, and which includes means forvibrating a workpiece in Va fixed plane relative thereto to effectsubstantial longitudinal alignment of the workpiece portions.

It is a further object of the invention to provide a machine adapted toaccommodate and straighten a small workpiece in at least two planesrelative thereto by vibrating the workpiece in planes passing throughits longitudinal axis to effect straightening of the same with nosubstantial endwise movement thereof.

The drawings show a preferred embodiment of the invention and suchembodiment will be described, but it will be understood that variouschanges may be made from the construction disclosed, and that thedrawings and description are not to be construed as defining or limitingthe scope :of the invention, the claims forming a part of thisspecification being relied upon for that purpose.

Of the drawings:

FIG. 1 is a fragmentary perspective view of a straightening machineconstituting a presently preferred embodiment of the invention andshowing the general arrangement of the Work holders.

FIG. 2 is a fragmentary transverse vertical section taken as indicatedby the line 2 2 of FIG. 1, showing a iirst group work holder.

FIG. 3 is a fragmentary transverse vertical section taken as indicatedby the line 3-3 in FIG. 1, showing a second group work holder.

FIG. 4 is a fragmentary plan view of the work holders of FIG. 1 showinga workpiece therein bent to an undulating shape, the position of theworkpiece in an alternate portion of the operating cycle being indicatedby broken lines.

FIG. 5 is a fragmentary transverse vertical section taken as indicatedby the line 5 5 in FIG. l, showing means for moving the Work holders,and a 'means for adjustably ,controlling workiholder movement.

FIG. 6 is a fragmentary side view, partially broken Aaway as generallyindicated by the line 6-6 in FIG. 5,

showing the mechanism of FIG. 5.

Generally speaking, the straightening machine of the presentinventioncomprises at least three work holders which are positioned inseries along a longitudinal axis and which are respectively adapted tovengage successive longitudinally spaced portions of an elongatedworkpiece 'arranged with its centerline in general alignment with the.ing of the workpiece in at least two planes. Also included UnitedStates Patent O in the machine is a power means for varying themagnitude of transverse displacement of the said workpiece portionsbetween a position of maximum displacement and a position wherein theworkpiece portions are substantially longitudinally aligned. Stillfurther, a manual adjustable controlling means is provided forpreselecting the maximum magnitude of work holder movement.

In the straightening operation, the workpiece is first held straight inone channel with the centerline of the workpiece in general alignmentwith the longitudinal axis of the work holders. The workpiece is thenvibrated by transversely displacing the centerline portions thereof,associated with the moving work holders, to one and the opposite side ofsaid axis while the magnitude of transverse displacement is variedbetween a position of maximum workpiece centerline displacement and aposition wherein the workpiece portiops are substantially longitudinallyaligned. Thereafter, the workpiece may be positioned in the otherchannel and the operation repeated to atfect substantial longitudinalalignment of the workpiece portions in a second plane thereof. Thealternate bending operations cause the workpiece to assume a permanentlystraight set. The machine constituting the presently preferredembodiment of the invention is particularly suited for straighteningsmall workpieces with no substantial endwise movement of the workpieceoccurring during the straightening operation, however, it is notnecessarily restricted to such application and may be adapted toaccommodate elongated workpiece for axial passage therethrough.

Referring now to FIG. l, it will be noted that the straightening machineillustrated therein includes a plurality of work holders indicatedgenerally at 10. The work holders 10, 10 are arranged in a longitudinalseries along a longitudinal axis 12 fixed relative to a machine frame14.

It will be noted that the plurality of work holders designated generallyas 10 includes two groups of work holders alternately arranged inlongitudinal series along the aforementioned axis 12. The iirst group ofwork holders comprises four similar work holders, each of which isdesignated by the reference numeral 16, whereas the second group of workholders comprises four similar work holders each respectively designatedby the reference numeral 18. The total number of work holders employedin practicing the invention is optional; however, it is evident that thenumber employed may be somewhat dependent upon vthe length of theelongated workpiece to be straightened, particularly where thestraightening operation is to be performed with no substantial endwisemovement of the workpiece. It should be noted that at least three workholders will be employed in practicing the invention.

Referring to FIG. 2, wherein a iirst group work holder 16 is shown, itwill be noted that the said wor-k holder comprises a pair oftransversely aligned members 20, 20 having transversely spaced opposedinner radial edge surfaces 22, 22, and 24, 24 which surfacesrespectively define portions of a first channel 23 and a second channel25. Each of the two channels, is adapted to receive an associatedportion of an elongated workpiece. Each of the members 20, 20l alsoincludes abutting inner edge surfaces 26, 26 and 27, 27, a lower edgesurface 28, 28 and a longitudinally disposed shoulder surface 30, 30. Agenerally H-shaped press plate 32 fastened to the machine frame 14defines a shallow rectangular recess 34 with a fiat bottom surface 36generally centrally positioned Within the upper surface thereof forreceiving the Work holders in longitudinal alignment therein and alsoincludes transversely extending end portions 38, 38 for supporting apair of lever shafts or pins 40, 40'. A pair of press levers 42, 42,which will be hereinafter further described, are pivotally mounted onthe said shafts. A pair of elongated hardened tool steel liner bars 44,44 are positioned in longitudinal parallel alignment along thetransversely spaced side surface portions of the recess 34. The shouldersurfaces 30, 30 of the members 20, abut the liner bars 44, 44 therebyserving to secure the first group work holders against transversemovement within the recess. At this point, it should be noted that thepress levers 42, 42 do not engage the first group work holders.

Each of the second group work holders 18, 18, best shown in FIG. 3,comprises a pair of transversely aligned members 46, 46 havingtransversely spaced opposed radial inner edge surfaces 22, 22 and 24, 24partially defining a first channel 23 and a second channel 25respectively, each of the said channels being identical in bothconfiguration and function to a corresponding channel defined by thelirst group work holders. Each of the members 46, 46 further includesabutting edge surfaces 48, 48 and 49, 49, a lower surface 50, 50, alongitudinally disposed outer edge surface 52, 52 which slants outwardlyand downwardly from the vertical and a longitudinally disposed shouldersurface 54, 54. A pair of vertically adjustable wedges 56, 56 havinginclined inner edge surfaces 58, 58 associated with and complementary tothe inclined outer edge surfaces 52, 52 provide for adjustableengagement between the second group work holders 18, 18 and the presslevers 42, 42 to facilitate alignment of the movable second group workholders with the stationary first group ones. It should be noted thatwhen the members 46, 46 are positioned within the recess 34 with thelower surfaces 50, 50 slidably engaging the fiat surface 36 there isclearance 60, 60 between lthe shoulder surfaces 54, 54 and the linerbars 44, 44. Thus, it will be evident that the second group work holders18, 18 are slidably movable upon the flat surface 36 between limitsestablished by the hardened tool steel liner bars 44, 44 which serve tobuffer work holder movement. A pair of transversely spacedlongitudinally aligned hold down bars 62, 62 fastened to the press plate32 in position immediately above the work holders secure the workholders against vertical movement. As previously mentioned, the totalnumber of work holders employed in practicing the invention is optional,and when less than the total number that can be accommodated within therecess 34 is used a plurality of filler bars 64, 64 are employed to fillthe space within the recess not occupied by work holders, therebysecuring the work holders against longitudinal movement within therecess as shown in FIG. 1.

In FIG. 4, a workpiece 66 is shown positioned within the first channel23. The movable work holders 18, 18 are shown in a position of maximumleftwardly transverse displacement relative to the stationary firstgroup work holders 16, 16. The portions of the workpiece engaged by thesecond group work holders 18, 18 are transversely displaced causing theworkpiece to assume an undulating shape. The resulting condition canbest be seen by observing the displacement of the workpiece centerline68 relative to the stationary axis 12. The position of the workpiecewhen two holders have assumed the position of maximum rightwardlytransverse displacement is indicated by broken lines. Thus, it should beapparent that the reciprocal motion of the movable tool holders relativeto the stationary ones impart a vibratory motion to the workpiece bymoving the centerline thereof between a position of maximum transversedisplacement and an intermediate position wherein the portions of theworkpiece centerline are substantially longitudinally aligned. Withregard to FIG. 4, it should be further noted that the contour radius ofthe inner edge surface 22, 22 is smaller than the maximum radial bendassumed by the associated portion of the workpiece in its maximumundulated position so that the vertically disposed edges of the workholder do not contact the workpiece surface.

This arrangement minimizes the risk of workpiece surface damage.

Simultaneous reciprocal transverse movement of the work holders 18, 18may obviously be provided for in a variety of ways. In the presentlypreferred embodiment of the invention this movement is effected by apower operated lever system as best seen in FIG. 5. The lever systemgenerally comprises a pair of first class levers 42, 42 arranged forparallel oscillation on a pair of first axes 72, 72, which parallel thework holder axis 12 and which are fixed relative thereto, for operablyengaging the work holders 18, 18. A third class lever 74 is arranged foroscillation about a second axis 76 parallel to the work holder axis 12and movable relative thereto, for transmitting power to the first classlevers 42, 42. Power is transmitted from the third class lever 74 to thefirst class levers 42, 42 at the axes 77, 77, which are aligned inparallel with the work holder axis 12 and movable relative thereto. Apower operated eccentric means 78, which cooperates with the lever 74 totranslate the rotary motion of the eccentric shaft to an oscillatorymotion in the lever system, is preferably employed to drive the leversystem. The eccentric means 78 is arranged for rotation about a thirdaxis 80 parallel to the work holder axis 12 and fixed relative thereto.The aforementioned power means for varying the magnitude of work holdermovement is preferably a solenoid operated double acting air motor 82having a reciprocating part 84 operably connected to the movable secondaxis 76, which is the primary fulcrum of the lever system, and astationary part 86 secured to the machine frame. It should be apparentthat movement of the axes 76 and 77, 77 relative to the fixed axes 80and 72, 72 alters the mechanical advantage of the lever system therebyvarying the extent or magnitude reciprocal motion of the work holders18, 18. Also included in the machine is a manual adjustable controllingmeans for preselecting the maximum magnitude of work holder movement,which controlling means is preferably an adjustable microswitch 87mounted in the path of travel of the reciprocating part on the air motor82 for operating an electrical solenoid which, in turn, actuates an airvalve to reverse the direction of travel of the reciprocating part. Theaforementioned generally described operating mechanisms will behereinafter more specifically defined.

Referring now to the FIGS. 5 and 6 it will be seen that a pair oflongitudinally spaced side plates 88, 88 are fastened to the sideportions of the press plate 32 and extend vertically downward therefrom.Each of the said plates has therein defined a downwardly openinginverted U-shaped channel 90. A pair of hub bearings 92, 92 forjournalling the aforementioned eccentric means are fastened to the sideplates 88, 88 in longitudinal coaxial alignment above the channels 90,90. A pair of rectangular bearing blocks 94, 94 having channeledtransverse side edge portions 96, 96 adapted to engage the transverseedge surfaces of the channel are positioned within the said channel forrectilinear vertical slidable movement therein. The bearing blocks 94,94 have longitudinally coaxially aligned bores 98, 98 adapted to receivethe opposite end portions of a cylindrical pusher shaft in press titassembly therewith. A pair of set screws 99, 99 lock the pusher shaft inassembly with the drawing blocks. The shaft 100 serves as a fulcrum forthe third class lever 74, and also has assembled thereon a pusher yoke101 which operably connects the lever system with the aforementionedpower means for varying the magnitude of work holders movement, whichpower means will hereinafter be further described. The pusher yoke 101is a generally T-shaped member including a vertical downwardly extendingportion 105 and a cross bar portion 107, and a pair of spaced apartcentrally bored coaxially aligned cylindrical members 109, 109 welded tothe upper surface of the cross bar 107 at the outer end portionsthereof, adapted to receive the shaft 100 for assembly therewith. Thepreviously generally described third class lever 74, is morespecifically defined as a bearing yoke 74 comprising an elongatedgenerally vertically disposed bifurcated member defining an upwardlyopening U-shaped channel 102 and further including a longitudinallyaligned central bore in the lower end portion thereof, said bore havingtherein a bushing 111 adapted to receive the shaft 100. The bearing yokeis assembled with the shaft 100 intermediate the cylindrical members109, 109 and is thus arranged for oscillation on the shaft, said shaftalso having been previously generally referred to as the axis 76 and theprimary fulcrum of the lever system. A pair of transversely spacedlongitudinally axially aligned knuckle joints 104, 104 are pivotallyconnected to the upper outer edge portions of the bearing yoke. To theknuckle joints 104, 104 are fastened a pair of bearing pads 106, 106 fortransmitting the oscillatory motion of the bearing yoke to the firstclass levers 42, 42 to be hereinafter more fully described. Thebifurcated upper ends of the bearing yoke are rigidly connected by ayoke spacer 108.

As aforementioned, the press levers 42, 42 also previously referred toas first class levers comprise a pair of transversely spaced elongatedmembers having opposing interior edge surfaces. Radially contouredopposing inner surface portions 110, 110 are provided on the upper endportions of the press levers for operably engaging associated adjustingwedges 56, 56 on a work holder 18, 18. A longitudinally disposed recess112 partially defined by a flat surface portion 114 is defined in thelower interior surface portion of each of the press levers for receivingan associated bearing pad 104 in slidable engagement therewith. Each ofthe levers 42, 42 further includes a downwardly extending pin 113 on thelower end thereof. As stated above, the levers 42, 42 are pivotallymounted on the lever shafts 40, 40 which shafts are assembled by pressfit within the end portions 38, 38 of the plate 32. A tension spring 115connecting the pins 113, 113 urges the lower end portions of the levers42, 42 into engagement with the associated bearing pads 106, 106.

In accordance with the presently preferred practice, the operation ofthe straightening machines as set forth above is effected by a poweroperated eccentric means. The eccentric means indicated generally lbythe numeral 78 generally comprises an eccentric bearing block 116 and aneccentric shaft 118. The eccentric block 116 is an elongated block ofgenerally rectangular cross section having a longitudinal central bore120 adapted to receive an eccentric portion of the shaft 118 andincluding vertically disposed channels 122, 122 defined within thelongitudinally disposed side edge surfaces thereof adapted for verticalslidable lengagement within the channel 102 of the yoke 74. Theeccentric shaft 118 is journalled at the end portions thereof within thehub bearings 92, 92 and includes a generally longitudinal eccentricportion 124 intermediate the ends thereof coaxially extending throughthe bore 120. vA plurality of needle bearings contained within thebearing hubs 92, 92 and the bore 120 provide means for journalling theend portions and the eccentric portion of the shaft 118. Power means forrotating the eccentric shaft is preferably provided by a variable speeddrive motor 126 mounted on the machine frame 14 and coupled to theeccentric shaft by a universal coupling 128.

In operation, the eccentric means 78 cooperates with the yoke 74 totranslate the rotary motion of the shaft 118 to an oscillatory motion ofthe yoke 74, said motion being transmitted to the press levers 42, 42 bythe bearing pads 106, 106 to cause parallel oscillation of the presslevers. The adjustable wedges 56, 56 cooperate with the radiallycontoured surface portions 110, 110 of the press levers 42, 42 totranslate the oscillatory motion of the press levers to a reciprocalmotion. The reciprocalV motion is imparted to the tool holders 18, 18 tomove them -in unison.

In the presently preferred embodiment of the invention, the power meansfor varying the magnitude 0f work holder movement is preferably asolenoid actuated double acting air cylinder 82 having a cylinderportion 86 mounted on the frame 14 and a movable piston rod 84 arrangedfor vertical reciprocal movement. A link 130 threadably connected to theupper end portion of the piston rod 84 and locked in position relativethereto by a locking nut 132 provides operable connection with thepusher yoke 101, said yoke being secured at its downwardly extendingportion 105 to the link by a pin 134. Thus, the vertical reciprocalmovement of the piston rod 84 is transmitted to the fulcrum 76 by thepusher yoke 101 causing the bearing yoke 74 to move generally verticallyupward. The U-shaped channel 102 moves vertically upward relative to theeccentric bearing block 116 in slidable engagement therewith. Thebearing pads 106, 106 pivotally connected to the bearing yoke also movevertically upward in slidable engagement with the surfaces 114, 114defined by the press levers 42, 42. It should be apparent that movementof the axis 76 results in relative movement between the movable axes 76and 72, 72 and the fixed axes 80 and 77, 77 which varies the mechanicaladvantage of the lever system and which, in turn, varies the extent ormagnitude of the reciprocal movement of the work holders 18, 18.

As previously noted, a manually iadjustable control means forpreselecting the maximum magnitude of work holder movement is alsoincluded in the aforedescribed machine. The adjustable control means ispreferably a microswitch 87 secured to a bracket 136 which is slidablymounted upon an adjustment -r-od 138, positioned in parallel alignmentwith the piston rod 84, and which is releasably secured thereto by athumb screw 140. A trip lever 142 secured to the piston rod 84 inalignment with the microswitch 87 engages and thereby actuates themicroswitch as the piston rod moves vertically upward. The microswitch87 is electrically connected to a solenoid operated air valve whicharrests the upward travel of the piston rod 84 and reverses its-direction of travel when the microswitch is actuated. The adjustmentrod 138 has indicia 144 thereon indicating work holder movement so thatthe maximum magnitude of the work holder movement may be predeterminedby manually positioning the microswitch bracket 136 in selected positionrelative to-the adjustment bracket 138.

The machine preferably idles with the drive motor 126 in continuousoperation and the piston rod 84 in its maximum downwardly position, asshown in FIGS. 5 and 6. Thus, the eccentric means 78 continuouslyimparts a slight motion t-o the lever system; however, the adjustablewedges 56, 56 on the outer end portions of the movable work holders 18,18 are so adjusted that this idling motion is not transmitted to thework holders. Preferably, a manually operable switching means,independent of the drive motor starting circuit, is provided to energizethe air motor 82, thereby starting the -operating cycle by causing thereciprocating part or piston rod 84, and the mechanism associatedtherewith, to move upwardly. When the piston rod reaches the preselectedposition of maximum upwardly travel, as determined lby the adjustablypositioned microswitch 87, the trip lever 142 contacts the microswitch,thereby reversing the direction of piston rod motion causing the pistonrod to return to its maximum downwardly position completing the cycle.

The invention claimed is:

1. In a vibratory straightening machine for straightening elongatedworkpieces the combination comprising at least three work holderspositioned in series along a longitudinal axis, said work holders beingadapted to engage successive longitudinally spaced portions of Vanelongated workpiece arranged with its centerline in general alignmentwith said axis, means for moving at least one of the said work holdersrelative to another of said work holders transversely of said axis tovibrate the workpiece by displacing said centerline of the workpiece toone and the opposite side of said axis, and means for varying themagnitude of said work holder movement between a position of maximumcenterline displacement and a position wherein said workpiece portionsare substantially longitudinally aligned while the workpiece is beingvibrated.

2. In a vibratory straightening machine for straightening elongatedworkpieces the combination of at least three work holders comprisingfirst and second groups of work holders arranged in alternate seriesalong a fixed longitudinal axis, said work holders being adapted toengage successive longitudinally spaced portions of a workpiece, each ofthe said work holders in said first group being secured againstmovement, each of the said work holders in said second group beingarranged for reciprocal transverse movement relative to said axis, meansfor transversely reciprocating said work holders in said second group tovibrate said workpiece in a plane fixed relative thereto and means forvarying said transverse movement of said second group work holders toeffect substantial longitudinal alignment of the workpiece portions.

3. In a vibratory straightening machine for straightening elongatedworkpieces the combination of at least three work holders aligned inseries along a fixed longitudinal axis, said work holders definingtherein first and second channels in longitudinal alignment with saidaxis, said channels being adapted to longitudinally receive an elongatedWorkpiece with the centerline thereof in general alignment with saidaxis, said first channel being adapted to receive the workpiece with amajor dimension of the cross section thereof substantially verticallydisposed, said second channel being adapted to receive the workpiecewith the major dimension of the cross section thereof substantiallyhorizontally disposed, and means for reciprocally moving at least one ofthe work holders relative to another transversely of said axis tovibrate said workpiece by displacing said centerline of the workpiece toone and the opposite side of said axis to effect substantiallongitudinal alignment -of the workpiece in at least two planes thereof.

4. In a vibratory straightening machine for straightening elongatedworkpieces the combination of at least three work holders comprisingfirst and second groups of work holders arranged in alternate seriesalong a fixed longitudinal axis, said work holders defining thereinfirst and second channels in longitudinal alignment with said axis, saidchannels `being adapted to receive an elongated workpiece with thecenterline thereof in general alignment with said axis, said firstchannel being adapted to receive the workpiece with a major dimension ofthe cross section thereof substantially vertically disposed, said secondchannel being adapted to receive the workpiece with the major dimensionof the cross section thereof substantially horizontally disposed, eachof the said work holders in said first group being secured againstmovement, each of the said work holders in said second group beingarranged for reciprocal transverse movement relative to said axis, meansfor transversely reciprocating said work holders in said second group tovibrate said workpiece in a plane fixed relative thereto, and means forvarying said transverse movement of said second group work holders toeffect substantial longitudinal alignment of the workpiece in at leasttwo planes thereof.

5. A vibratory straightening machine for straightening elongatedworkpieces comprises at least three work holders positioned in seriesalong a longitudinal axis, said work holders being 'adapted to engagesuccessive longitudinally spaced portions of an elongated workpiecearranged with its centerline in general alignment with said axis, meansfor moving at least one of the said work holders relative to another -ofsaid work holders transversely of said axis to vibrate the workpiece bydisplacing said centerline of the workpiece to one and the opposite sideof said axis, means for varying the magnitude of said work holdermovement between a position of maximum centerline displacement and aposition wherein said workpiece portions are substantiallylongitudinally aligned while the workpiece is being vibrated, andmanually adjustable controlling means for preselecting said maximummagnitude of said work holder movement.

6. The combination defined in claim 1 further characterized by saidmeans for moving at least one of said work holders being adjustable.

7. The combination defined in claim 1 further characterized by saidmeans for moving at least one of said work holders including eccentricmeans, and a lever system operated by said eccentric means, said leversystem being operably connected to said one work holder.

8. The combination defined in claim 7 further characterized by saidmeans for varying said work holder movement including power meansoperably connected to a fulcrum means in said lever system for movingsaid fulcrum means relative to said eccentric means.

9. A vibratory straightening machine as set forth in claim 5, whereinsaid means for moving `at least one of said work holders includes afirst class lever arranged for oscillation about a first axis parallelto said longitudinal axis and fixed relative thereto, said first classlever having first and second end portions, said first end portion beingoperably connected to said movable work holder, a third class leverarranged for oscillation about a second axis parallel to saidlongitudinal axis and movable relative thereto, said third class leverincluding an oscillating end portion operably connected to said secondend portion of said first class lever, and eccentric means rotatableabout a third axis parallel to said longitudinal axis and fixed relativethereto, said eccentric means arranged to operably engage said thirdclass lever between said second axis and said oscillating end portion.

10. A vibratory straightening machine as set forth in claim 9, whereinsaid means for varying said magnitude of said work holder movementincludes a motor having a stationary part and a reciprocating part, saidstationary part being secured in a position fixed relative to saidlongitudinal axis, said reciprocating part being operably secured tosaid second axis for moving said second axis in parallel relation tosaid longitudinal axis.

11. A vibratory straightening machine as set forth in claim 10, whereinsaid manually adjustable controlling means includes Ian adjustablypositioned switching means actuated by said reciprocating part forreversing the direction of motion of said reciprocating part.

12. A vibratory straightening machine as set forth in claim 11, whereinsaid manually adjustable controlling means includes manually operableswitching means for energizing said motor.

13. In a vibratory straightening machine for straightening elongatedworkpieces, the combination comprising a machine frame having asubstantially fiat surface, at least three work holders supported onsaid fiat surface in series along a longitudinal axis fixed relative tosaid frame, said work holders including first and second group -of workholders each of the said first group work holders being secured on saidfiat surface against movement relative thereto, each of the said secondgroup work holders being slidably movable on said fiat surfacetransversely relative to said axis, each of the said work holderscomprising a pair of transversely aligned members having transverselyspaced opposing inner edge surfaces adapted to engage associatedportions of an elongated workpiece arranged therebetween with itscenterline in general alignment with said longitudinal axis, each of thesaid second group work holders having outer end portions transverselydisposed from said axis, power means for moving said second group workholders to vibrate the workpiece by alternately displacing thecenterline of the workpiece to one and the opposite side of said axis,and means for varying said movement of said second group work holders toeffect substantial longitudinal alignment of the workpiece portions.

14. The combination dened in claim 13 further characterized by saidinner edge surfaces defining r'st and second channels in longitudinalalignment with said axis, said rst channel being adapted to receive theworkpiece with a major dimension of the cross section thereofsubstantially perpendicular to said at surface, said second channel-being adapted to receive the workpiece with the major dimension ofthe`cross section thereof substantially parallel to said flat surface.

10 and a lever system -operated by said eccentric means, said levermeans operably engaging said outer end portions of said second groupwork holders for moving said work holders in unison.

16. The combination dened in claim 15 further characterized by saidlouter end portions being adjustable.

CHARLES W. LANHAM, Primary Examiner.

15. The combination dened in claim 13 further char- 15 R D- GREFE,ASSSHU Examineracterized by said power means including eccentric means,

1. IN A VIBRATORY STRAIGHTENING MACHINE FOR STRAIGHTENING ELONGATEDWORKPIECES THE COMBINATION COMPRISING AT LEAST THREE WORK HOLDERSPOSITIONED IN SERIES ALONG A LONGITUDINAL AXIS, SAID WORK HOLDERS BEINGADAPTED TO ENGAGE SUCCESSIVE LONGITUDINALLY SPACED PORTIONS OF ANELONGATED WORKPIECE ARRANGED WITH ITS CENTERLINE IN GENERAL ALIGNMENTWITH SAID AXIS, MEANS FOR MOVING AT LEAST ONE OF THE SAID WORK HOLDERRELATIVE TO ANOTHER OF SAID WORK HOLDERS TRANSVERSELY OF SAID AXIS TOVIBRATE THE WORKPIECE BY DISPLACING SAID CENTERLINE OF THE WORKPIECE TOONE AND THE OPPOSITE SIDE OF SAID AXIS, AND MEANS FOR VARYING THEMAGNITUDE OF SAID WORK HOLDER MOVEMENT BETWEEN A POSITION OF MAXIMUMCENTERLINE DISPLACEMENT AND A POSITION WHEREIN SAID WORKPIECE PORTIONSARE SUBSTANTIALLY LONGITUDINALLY ALIGNED WHILE THE WORKPIECE IS BEINGVIBRATED.